WO2023152854A1 - Compresseur et dispositif de cycle de réfrigération - Google Patents

Compresseur et dispositif de cycle de réfrigération Download PDF

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Publication number
WO2023152854A1
WO2023152854A1 PCT/JP2022/005282 JP2022005282W WO2023152854A1 WO 2023152854 A1 WO2023152854 A1 WO 2023152854A1 JP 2022005282 W JP2022005282 W JP 2022005282W WO 2023152854 A1 WO2023152854 A1 WO 2023152854A1
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WO
WIPO (PCT)
Prior art keywords
annular member
oil
refrigerant
hole
guide wall
Prior art date
Application number
PCT/JP2022/005282
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English (en)
Japanese (ja)
Inventor
秀明 北川
Original Assignee
三菱電機株式会社
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Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2022/005282 priority Critical patent/WO2023152854A1/fr
Publication of WO2023152854A1 publication Critical patent/WO2023152854A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/04—Measures to avoid lubricant contaminating the pumped fluid

Definitions

  • the present disclosure relates to a compressor and a refrigeration cycle device having a sealed container having an oil reservoir space at the bottom.
  • a compression mechanism, an electric motor, and a drive shaft for transmitting the rotational force of the electric motor to the compression mechanism are provided in a closed container.
  • the compressor stores refrigerating machine oil (hereinafter referred to as oil) in an oil reservoir space at the bottom of the closed container.
  • oil refrigerating machine oil
  • By sealing the it is possible to compress the refrigerant in the compression mechanism.
  • low-pressure refrigerant sucked into the sealed container from the suction pipe is compressed by the compression mechanism to become high-pressure refrigerant, and the high-pressure refrigerant is once discharged from the compression mechanism into the sealed container and then discharged into the discharge pipe. is discharged out of the closed container.
  • the high-pressure refrigerant discharged from the compression mechanism contains oil, and the oil is discharged out of the sealed container together with the high-pressure refrigerant.
  • the rotation of the electric motor causes a swirling flow of the refrigerant in the closed container.
  • the swirling flow may collide with the oil in the oil sump space and atomize the oil.
  • the atomized oil is sometimes mixed with the gaseous refrigerant in the closed container and discharged out of the closed container in large amounts together with the refrigerant.
  • Patent Document 1 a plate-shaped annular member is arranged so as to cover an oil reservoir space, and a plurality of baffle plates having a large number of pores are erected and fixed to the annular member at intervals in the circumferential direction. are doing.
  • Patent Document 1 discloses that the swirling flow collides with the baffle plate instead of the oil in the oil reservoir space to separate the oil from the refrigerant, and the separated oil is transferred to the gap between the annular member and the drive shaft. The amount of oil discharged to the outside of the sealed container is reduced by dropping the oil into the oil reservoir space.
  • the compressor of Patent Document 1 has a configuration in which a plurality of baffle plates are fixed to an annular member, so there is a problem that the number of parts increases.
  • the present disclosure has been made to solve the above-described problems, and an object of the present disclosure is to provide a compressor and a refrigeration cycle device that can reduce the number of parts and reduce the amount of oil discharged out of the sealed container. It is.
  • a compressor includes a closed container having an oil reservoir space at the bottom, a compression mechanism arranged in the closed container for compressing a refrigerant, an electric motor arranged below the compression mechanism, and rotation of the electric motor. It has a drive shaft that transmits force to the compression mechanism, and a plate-like main body that has a through hole through which the drive shaft passes. and a plate-shaped annular member disposed between the annular member, and the body portion of the annular member includes a passage hole for passing the refrigerant above the annular member to the lower side of the annular member, and a passage hole of the annular member.
  • a plate-like air guide wall is formed to guide the coolant from above to the passage hole, and the main body and the air guide wall are integrally formed.
  • a refrigeration cycle apparatus includes the compressor, condenser, pressure reducer, and evaporator.
  • the compressor suppresses oil splashing in the oil sump space by the body portion of the annular member, and actively removes the oil existing above the annular member by the wind guide wall and the passage hole. It can lead to the oil sump space. Therefore, the compressor can reduce the amount of oil discharged to the outside of the sealed container. Further, in the annular member, since the main body and the wind guide wall are integrally formed, the number of parts can be reduced. In this way, the compressor can reduce the amount of oil discharged to the outside of the sealed container while reducing the number of parts.
  • FIG. 1 is a schematic vertical cross-sectional view showing a compressor according to Embodiment 1;
  • FIG. FIG. 2 is a partially enlarged view of FIG. 1;
  • FIG. 4 is an explanatory diagram of flow paths formed between a guide frame and a closed container of the compressor according to Embodiment 1;
  • 2 is a perspective view of a subframe and an annular member of the compressor according to Embodiment 1.
  • FIG. FIG. 2 is a schematic cross-sectional view taken along line AA of FIG. 1; 4 is a partial schematic perspective view of an annular member of the compressor according to Embodiment 1.
  • FIG. FIG. 8 is a partial schematic perspective view of an annular member of a compressor according to Embodiment 2;
  • FIG. 10 is a schematic configuration diagram of a refrigeration cycle apparatus according to Embodiment 3;
  • FIG. 1 is a schematic vertical cross-sectional view showing a compressor according to Embodiment 1.
  • FIG. 2 is a partially enlarged view of FIG. 1.
  • FIG. 3 is an explanatory diagram of flow paths formed between the guide frame and the closed container of the compressor according to Embodiment 1.
  • FIG. The configuration of the compressor 100 will be described below with reference to FIGS. 1 to 3.
  • FIG. 1 is a schematic vertical cross-sectional view showing a compressor according to Embodiment 1.
  • FIG. 2 is a partially enlarged view of FIG. 1.
  • FIG. 3 is an explanatory diagram of flow paths formed between the guide frame and the closed container of the compressor according to Embodiment 1.
  • FIG. The configuration of the compressor 100 will be described below with reference to FIGS. 1 to 3.
  • the compressor 100 is a so-called vertical scroll compressor, and the axial direction of the compressor 100 is the Z direction, which is the vertical direction in FIG.
  • the compressor 100 compresses and discharges a refrigerant, which is a working gas.
  • a refrigerant for example, R407C refrigerant, R410A refrigerant, R32 refrigerant, or the like is used.
  • the compressor 100 includes a closed container 1 having an oil reservoir space 5 at the bottom, a compression mechanism section 2 having a fixed scroll 4 and an orbiting scroll 3, an electric motor 16, and a drive shaft 19.
  • This compressor 100 is one of the components of a refrigeration cycle used in various industrial machines such as refrigerators, freezers, air conditioners, refrigeration systems, and water heaters.
  • the direction in which the drive shaft 19 extends is called the axial direction
  • the direction perpendicular to the axial direction is called the radial direction
  • the direction around the drive shaft is called the circumferential direction.
  • a compression mechanism 2, an electric motor 16, and a drive shaft 19 are accommodated in the closed container 1.
  • the high-pressure refrigerant gas compressed by the compression mechanism 2 is discharged into the high-pressure gas atmosphere 6 inside the sealed container 1 .
  • This refrigerant gas is configured to circulate through a refrigeration cycle circuit in which the compressor 100 is incorporated.
  • the sealed container 1 is formed, for example, in a cylindrical shape and has pressure resistance.
  • the sealed container 1 is formed to extend vertically.
  • a suction pipe 7 is connected to the side surface of the sealed container 1 for taking the refrigerant into the sealed container 1 .
  • a discharge pipe 11 for discharging the compressed refrigerant from the closed container 1 to the outside is connected to the other side surface of the closed container 1 .
  • a suction check valve 9 and a spring 10 are arranged inside the suction pipe 7 .
  • the suction check valve 9 is urged by a spring 10 in a direction to close the suction pipe 7 and prevents the refrigerant from flowing backward.
  • the sealed container 1 has a high-pressure gas atmosphere 6 filled with high-pressure gas compressed by the compression mechanism 2 inside the closed container 1 .
  • the sealed container 1 also has an oil reservoir space 5 for storing refrigerating machine oil (hereinafter referred to as oil) at the bottom of the sealed container 1 .
  • the oil sump space 5 is located within a high-pressure gas atmosphere 6 .
  • the oil sump space 5 is a space below the sub-frame 37 that supports the lower end of the drive shaft 19 in the closed container 1 .
  • the drive shaft 19 is supported by a thrust bearing 28 provided on the lower end surface of the drive shaft 19 .
  • Thrust bearing 28 is fixed to holder 29 fixed to sub-frame 37 .
  • An annular member 50 for reducing the amount of oil discharged out of the closed container is attached to the lower portion of the sub-frame 37 by, for example, a fastener (not shown). The details of the ring member 50 will be explained again.
  • the compression mechanism section 2 is a section that compresses the refrigerant sucked into the sealed container 1 from the intake pipe 7 and has an orbiting scroll 3 and a fixed scroll 4 .
  • the fixed scroll 4 is arranged on the upper side and the orbiting scroll 3 is arranged on the lower side.
  • the fixed scroll 4 has a fixed base plate 4b and a fixed spiral body 4a formed on the fixed base plate 4b.
  • the orbiting scroll 3 has an orbiting bed plate 3b and an orbiting spiral body 3a formed on the orbiting bed plate 3b.
  • the fixed scroll 4 and the orbiting scroll 3 are arranged so that the fixed spiral body 4a and the orbiting scroll body 3a face each other.
  • a compression chamber 2b is formed between the fixed spiral body 4a and the oscillating spiral body 3a by combining the fixed spiral body 4a and the oscillating spiral body 3a in opposite directions.
  • the fixed spiral body 4a of the fixed scroll 4 and the outer peripheral space of the base plate outside the orbiting scroll 3 (hereinafter referred to as the suction side space 8) are a low-pressure space of suction gas atmosphere of suction pressure.
  • the fixed scroll 4 is fixed with bolts (not shown) or the like to a guide frame 30 fixedly supported by the sealed container 1 .
  • a pair of two fixed-side Oldham ring grooves 15 a are formed in a straight line on the outer peripheral portion of the fixed scroll 4 .
  • a pair of two fixed-side keys 42a of the Oldham ring 40 are installed in the fixed-side Oldham ring groove 15a so as to be reciprocally slidable.
  • a cylindrical boss portion 3c is formed on the other surface of the oscillating base plate 3b of the oscillating scroll 3 opposite to the one surface on which the oscillating spiral body 3a is formed.
  • a swing bearing 26 is provided on the inner surface of the boss portion 3c. The swing shaft 21 of the drive shaft 19 is inserted into the swing bearing 26 , and the rotation of the swing shaft 21 causes the swing scroll 3 to revolve with respect to the fixed scroll 4 .
  • a compliant frame 31 is arranged in contact with the other surface of the rocking base plate 3b of the rocking scroll 3.
  • a thrust surface 33 of the compliant frame 31 and a thrust surface 3 d that can slide are formed on the other surface of the rocking base plate 3 b of the rocking scroll 3 .
  • a pair of rocking-side Oldham ring grooves 15b are formed in a straight line on the outer peripheral portion of the rocking scroll 3 .
  • the rocking-side Oldham ring groove 15b has a phase difference of about 90 degrees from the fixed-side Oldham ring groove 15a, and a pair of rocking-side keys 42b of the Oldham ring 40 are installed so as to be reciprocally slidable. .
  • the swing-side key 42 b reciprocates on a reciprocating sliding surface 41 formed on the outer periphery of the thrust surface 33 of the compliant frame 31 .
  • the rocking bed plate 3b is formed with an air bleed hole 3e penetrating from one surface on which the rocking spiral body 3a is provided to the other surface of the rocking bed plate 3b.
  • the air bleed holes 3e are composed of an air bleed inlet 3ei formed on the upper surface, which is one surface of the rocking base plate 3b, and an air bleed outlet formed on the lower surface, which is the other surface of the rocking base plate 3b. 3eo.
  • the bleed inlet 3ei opens into the compression chamber 2b.
  • the extraction outlet 3eo intermittently communicates with the gas introduction passage 14 provided in the compliant frame 31 .
  • the extraction outlet 3eo intermittently communicates with the gas introduction passage 14, so that intermediate-pressure gas refrigerant in the middle of compression in the compression chamber 2b flows through the extraction hole 3e and the gas introduction passage 14 into an intermediate pressure space 32b, which will be described later. (See FIG. 1).
  • the intermediate pressure refers to a pressure higher than the suction pressure and lower than the discharge pressure.
  • the air bleed hole 3e intermittently bleeds air from the compression chamber 2b in the middle of compression to the intermediate pressure space 32b as the orbiting scroll 3 revolves.
  • a guide frame 30 and a sub-frame 37 that holds the drive shaft 19 are fixed inside the sealed container 1 .
  • the guide frame 30 is positioned below the compression mechanism 2 and above the electric motor 16 .
  • the subframe 37 is positioned below the electric motor 16 .
  • a compliant frame 31 is housed inside the guide frame 30 .
  • a flow path 30c is formed through which the high-pressure gas refrigerant flowing out from the discharge port 12 formed in the fixed scroll 4 passes (FIGS. 1 and 3). 3).
  • the high-pressure gas refrigerant that has flowed out from the discharge port 12 is guided below the compression mechanism section 2 through the flow path 30c.
  • a high-pressure gas atmosphere 6 is formed in the sealed container 1 by guiding the high-pressure gas refrigerant downward from the compression mechanism section 2 .
  • An upper fitting cylindrical surface 30a is formed on the inner peripheral surface of the guide frame 30 on the compression mechanism 2 side.
  • the upper fitting cylindrical surface 30 a is engaged with an upper fitting cylindrical surface 35 a formed on the outer peripheral surface of the compliant frame 31 .
  • a lower fitting cylindrical surface 30 b is formed on the inner peripheral surface of the guide frame 30 on the electric motor 16 side, and the lower fitting cylindrical surface 30 b is formed on the outer peripheral surface of the compliant frame 31 . It is engaged with the mating cylindrical surface 35b.
  • An upper annular seal member 36 a and a lower annular seal member 36 b are arranged at two locations on the outer peripheral surface of the compliant frame 31 .
  • An upper annular seal member 36 a and a lower annular seal member 36 b partition between the inner surface of guide frame 30 and the outer surface of compliant frame 31 .
  • An intermediate pressure space 32b is formed by a space partitioned by the upper annular seal member 36a and the lower annular seal member 36b.
  • the compliant frame 31 supports the orbiting scroll 3 in the axial direction.
  • the compliant frame 31 has a thrust surface 33 that axially supports the thrust force acting in the axial direction of the orbiting scroll 3 .
  • the compliant frame 31 is formed with a gas introduction passage 14 that communicates between the space formed above the thrust surface 33 and the intermediate pressure space 32b.
  • the gas introduction passage 14 communicates with the bleed hole 3 e according to the orbital motion of the orbiting scroll 3 .
  • Intermediate-pressure refrigerant is introduced into the intermediate-pressure space 32b from the compression chamber 2b, which is in the middle of compression, by connecting the gas introduction passage 14 to the bleed hole 3e.
  • the bleed hole 3e is blocked by facing the thrust surface 33 of the compliant frame 31 according to the orbital motion of the orbiting scroll 3, thereby stopping the introduction of the intermediate-pressure refrigerant into the intermediate-pressure space 32b. .
  • the intermediate-pressure gas refrigerant flows from the compression chamber 2b to the intermediate-pressure space 32b. Introduction occurs intermittently.
  • the intermediate pressure space 32b becomes intermediate pressure by intermittently introducing the intermediate pressure gas refrigerant.
  • the compliant frame 31 axially supports the orbiting scroll 3 by the intermediate pressure in the intermediate pressure space 32b.
  • the intermediate pressure in the intermediate pressure space 32 b acts on the compliant frame 31 .
  • a high pressure from the high-pressure gas atmosphere 6 acts on the compliant frame lower end surface 34 .
  • the compliant frame 31 floats in the axial direction due to these pressures acting on the compliant frame 31 and has a function of pushing up the orbiting scroll 3 in the axial direction.
  • an intermediate-pressure boss portion outer space 38 is provided between the outside of the boss portion 3c of the orbiting scroll 3 and the compliant frame 31. Further, the compliant frame 31 is provided with an intermediate pressure regulating valve space 39d.
  • the intermediate pressure regulating valve space 39d accommodates an intermediate pressure regulating valve 39a for adjusting the pressure of the boss portion outer space 38, an intermediate pressure regulating valve retainer 39b, and an intermediate pressure regulating spring 39c.
  • the intermediate pressure adjusting spring 39c is contracted from its natural length and accommodated in the intermediate pressure adjusting valve space 39d.
  • the compliant frame 31 is provided with a through passage 39e that communicates between the boss portion outer space 38 and the intermediate pressure regulating valve space 39d.
  • a compliant frame upper space 32a is provided between the outer peripheral surface of the compliant frame 31 on the fixed scroll side (upper side in FIG. 1) of the intermediate pressure regulating valve space 39d and the inner peripheral surface of the guide frame 30. ing.
  • the compliant frame upper space 32a communicates with the intermediate pressure regulating valve space 39d.
  • the compliant frame upper space 32 a communicates with the space inside the Oldham ring 40 . Therefore, the boss portion outer space 38 and the inner space of the Oldham ring 40 communicate with each other via the through passage 39e, the intermediate pressure regulating valve space 39d, and the compliant frame upper space 32a.
  • the electric motor 16 rotates the drive shaft 19 .
  • the electric motor 16 is configured such that its operating frequency can be controlled by, for example, an inverter device.
  • the electric motor 16 has an electric motor rotor 16a and an electric motor stator 16b, and generates a rotational force with a variable rotational speed.
  • the motor rotor 16a is fixed to the drive shaft 19 by shrink fitting or the like.
  • the electric motor rotor 16a has a plurality of through passages 17a penetrating in the axial direction, and the plurality of through passages 17a are formed symmetrically or point-symmetrically with respect to the axis.
  • the motor rotor 16a and the motor stator 16b are positioned so that a minute gap 17c exists between them.
  • the electric motor stator 16b is connected to a glass terminal (not shown) fixed to the guide frame 30 via a lead wire (not shown) to obtain power from the outside.
  • the electric motor stator 16b is fixed to the closed container 1 by shrink fitting or the like, and a through passage 17b is formed by notching in the outer peripheral portion of the electric motor stator 16b.
  • the drive shaft 19 and the electric motor rotor 16a rotate with respect to the electric motor stator 16b when electric power is supplied to the electric motor stator 16b.
  • a balance weight 18a is fixed to the motor rotor 16a and a balance weight 18b is fixed to the drive shaft 19 in order to balance the entire rotation system of the compressor 100. As shown in FIG.
  • the drive shaft 19 has a swing shaft 21 forming the upper portion of the drive shaft 19 , a main shaft 20 forming the intermediate portion of the drive shaft 19 , and a sub shaft 22 forming the lower portion of the drive shaft 19 .
  • the main shaft 20 has a cylindrical structure, is fitted in a main bearing 25 provided on the inner peripheral surface of the compliant frame 31, and is rotatably supported.
  • the sub-shaft 22 is rotatably supported by a sub-bearing 27 provided on the inner peripheral surface of the sub-frame 37 .
  • the lower end surface of the secondary shaft 22 is supported by its own weight by a thrust bearing 28 .
  • Thrust bearing 28 is fixed to holder 29
  • holder 29 is fixed to sub-frame 37 .
  • the main bearing 25 and the sub-bearing 27 have a cylindrical structure and are made of, for example, sliding bearings such as a copper-lead alloy, and rotatably support the drive shaft 19 .
  • the drive shaft 19 transmits the rotational force generated by the electric motor 16 to the compression mechanism section 2 .
  • an oil supply passage 23 extending axially from the end of the drive shaft 19 and supply passages 24a and 24b extending radially from the oil supply passage 23 are formed inside the drive shaft 19 .
  • the oil supply passage 23 opens at the axial upper end of the drive shaft 19 .
  • a supply passage 24 a is formed in the sub shaft 22 and a supply passage 24 b is formed in the main shaft 20 .
  • the supply path 24b opens at a position covered by the main bearing 25 and supplies the main bearing 25 with oil.
  • a supply passage 24a of the subshaft 22 opens at a position covered with the subshaft 22 and supplies the subshaft 22 with oil.
  • the oil sucked up from the oil sump space 5 passes through the oil supply passage 23 and the supply passages 24a and 24b, and is supplied to sliding portions such as the main bearing 25, the swing bearing 26 and the sub-bearing 27.
  • thin arrows indicate the flow of oil.
  • FIG. 4 is a perspective view of a subframe and an annular member of the compressor according to Embodiment 1.
  • FIG. FIG. 5 is a schematic cross-sectional view taken along line AA of FIG.
  • the sub-frame 37 has a cylindrical portion 37a and fixed leg portions 37b radially projecting from the outer peripheral surface of the cylindrical portion 37a.
  • Three fixed leg portions 37b are formed on the outer peripheral surface of the cylindrical portion 37a at regular intervals in the circumferential direction.
  • a radially outer end surface of the fixed leg portion 37b is fixed to the inner peripheral surface of the sealed container 1 by welding or the like.
  • the number of fixing legs 37b is not limited to three, and may be two or four or more.
  • An annular member 50 for reducing the amount of oil discharged out of the closed container is attached to the lower surface of the sub-frame 37 by, for example, a fastener (not shown).
  • the annular member 50 is composed of a single plate-like metal plate.
  • the annular member 50 has an annular plate-shaped main body portion 52 with a through hole 51 formed in the center thereof, and the drive shaft 19 is passed through the through hole 51 to be stored in the electric motor 16 and the oil reservoir space 5 . placed between oil.
  • the body portion 52 is formed with a passage hole 53 through which the refrigerant in the annular member upper space 60 is passed toward the oil reservoir space 5 .
  • the main body portion 52 is formed with a passage hole 53 through which the refrigerant above the annular member 50 passes downwardly of the annular member 50 .
  • the passage hole 53 is configured as a through hole.
  • the body portion 52 has an outer diameter slightly smaller than the inner diameter of the closed container 1 as shown in FIG. This gap is provided to return the oil adhering to the inner peripheral surface of the sealed container 1 to the oil reservoir space 5 .
  • a plate-like wind guide wall 54 that guides the coolant above the annular member 50 to the passage hole 53 is formed in the body portion 52 .
  • the baffle wall 54 is formed by cutting and raising the body portion 52 upward.
  • a passage hole 53 is formed by a hole formed by cutting and raising the wind guide wall 54 from the body portion 52 .
  • the air guide wall 54 is configured in a rectangular shape and extends in the radial direction and the circumferential direction when viewed in the axial direction.
  • the rotation of the electric motor rotor 16a provided above the sub-frame 37 causes a swirling flow of refrigerant gas containing oil that has been compressed to a high pressure.
  • This swirl flow is a flow directed in the same direction as the rotation direction R of the electric motor rotor 16a.
  • the dotted arrow indicates the direction of the swirling flow.
  • the wind guide wall 54 is inclined upward toward the direction opposite to the rotation direction R so as to easily receive this swirling flow.
  • the baffle wall 54 has a fixed edge portion 54a connected to and fixed to the main body portion 52, and a non-fixed edge portion 54b separated from the main body portion 52. Fixed edge 54a is formed by one of the four edges and non-fixed edge 54b is formed by the other three of the four edges.
  • a fixed edge portion 54 a of the air guide wall 54 is provided in contact with the rotation direction R side of the electric motor rotor 16 a in the peripheral edge portion of the passage hole 53 .
  • At least one combination of the wind guide wall 54 and the passage hole 53 exists in the annular member 50 and is provided in the annular member 50 so as not to interfere with the sub-frame 37 .
  • the shape of the wind guide wall 54 is not limited to a rectangular shape. Each function and detailed dimensions of the air guide wall 54 and the passage hole 53 will be described later.
  • FIG. Outlined arrows in FIGS. 1 and 2 indicate the flow of the refrigerant.
  • a low-pressure (suction pressure) gas refrigerant is supplied from the suction pipe 7 toward the suction check valve 9, the gas refrigerant overcomes the spring force of the spring 10 and causes the suction check valve 9 to stop (not shown).
  • the suction check valve 9 is opened, and the gas refrigerant flows into the suction side space 8 inside the sealed container 1 .
  • the drive shaft 19 starts rotating when electric power is supplied to the electric motor 16 from the outside.
  • the rotation of the drive shaft 19 causes the swing shaft 21 to rotate, and the swing scroll 3 performs a swing motion (orbital motion).
  • the gas refrigerant is sucked into the compression chamber 2 b formed between the orbiting scroll 3 and the fixed scroll 4 .
  • the gas refrigerant is eventually boosted from low pressure to high pressure due to the geometric volume change of the compression chamber 2b. Thereafter, the gas refrigerant pressurized to a high pressure is discharged from the discharge port 12, passes through the flow path 30c, and is guided below the guide frame 30. As shown in FIG. The inside of the sealed container 1 becomes a high-pressure gas atmosphere 6 due to the gas refrigerant guided below the guide frame 30 . A high-pressure gas refrigerant inside the sealed container 1 is discharged to the outside through a discharge pipe 11 .
  • the bleed outlet 3eo of the bleed hole 3e of the oscillating bed plate 3b temporarily communicates with the gas introduction passage 14 due to the orbital motion of the oscillating scroll 3.
  • the bleed outlet 3eo of the bleed hole 3e is temporarily communicated with the gas introduction passage 14, whereby the intermediate-pressure gas refrigerant that is being compressed in the compression chamber 2b communicating with the bleed hole 3e is bled out of the compression chamber 2b. , through the gas introduction channel 14 into the intermediate pressure space 32b.
  • the temporary communication between the bleed hole 3e and the gas introduction passage 14 is intermittently performed while the orbiting scroll 3 revolves.
  • the intermediate pressure space 32b is a space sealed by an upper annular seal member 36a and a lower annular seal member 36b. Therefore, the intermediate-pressure gas refrigerant introduced into the intermediate-pressure space 32b floats the compliant frame 31 in the axial direction.
  • the intermediate pressure Pm1 in the boss outer space 38 is a combination of a predetermined pressure ⁇ determined by the elastic force of the intermediate pressure regulating spring 39c and the area exposed to the intermediate pressure of the intermediate pressure regulating valve 39a, and the pressure in the suction side space 8. It is the sum with Ps, which is Ps+ ⁇ . Further, the intermediate pressure Pm2 of the intermediate pressure space 32b is the product of a predetermined magnification ⁇ determined at the position of the compression chamber 2b communicating with the intermediate pressure space 32b and the pressure Ps of the suction side space 8, and is expressed as Ps ⁇ . Become.
  • the compliant frame 31 floats along the inner peripheral surface of the guide frame 30 in the axial direction.
  • the force due to this levitation is called pressing force.
  • the orbiting scroll 3 Due to the pressing force of the compliant frame 31, the orbiting scroll 3 is pushed up via the thrust surface 33 and floats. The levitation of the orbiting scroll 3 reduces the gap between the tip of each of the spiral bodies of the fixed scroll 4 and the orbiting scroll 3 forming the compression chamber 2b and the base plate. As a result, the high-pressure gas refrigerant is less likely to leak from the compression chamber 2b, and a highly efficient scroll compressor can be obtained.
  • the oil supplied to the main bearing 25 lubricates the main bearing 25 and then is led to the boss portion outer space 38 or the high-pressure gas atmosphere 6 .
  • the oil supplied to the boss portion 3 c of the orbiting scroll 3 lubricates the orbiting bearing 26 . led to.
  • the oil guided to the boss outer space 38 overcomes the spring force of the intermediate pressure regulating spring 39c when passing through the through passage 39e, pushes up the intermediate pressure regulating valve 39a, and temporarily enters the compliant frame upper space 32a. Ejected. After that, this oil is discharged inside the Oldham ring 40 and supplied to the suction side space 8 .
  • a part of the refrigerant discharged to the compliant frame upper space 32 a is supplied to the reciprocating sliding surface 41 after being supplied to the thrust surface 3 d and flows into the suction side space 8 .
  • the oil that has flowed into the suction side space 8 is sucked into the compression mechanism portion 2 together with the low-pressure gas refrigerant.
  • the sucked oil seals and lubricates the gaps between the fixed scroll 4 and the orbiting scroll 3 that constitute the compression mechanism 2, thereby enabling normal operation.
  • Excess oil in the compression mechanism portion 2 is discharged from the discharge port 12 of the compression mechanism portion 2 in a state of being contained in the refrigerant, passes through the flow path 30c along the flow of the refrigerant, and enters the compression mechanism portion. 2 below.
  • Refrigerant containing oil that has been guided downward from the compression mechanism portion 2 is guided to the annular member upper space 60 through the through passage 17b.
  • the annular member upper space 60 is a space below the electric motor 16 and above the sub-frame 37 . In the annular member upper space 60, a swirling flow is generated due to the rotation of the electric motor rotor 16a.
  • the compressor 100 does not have the annular member 50 , the swirling flow in the annular member upper space 60 collides with the oil in the oil sump space 5 .
  • the oil in the oil reservoir space 5 scatters and becomes misty, and the misty oil is mixed with the refrigerant and is discharged out of the sealed container as a result, increasing the amount of oil discharged out of the sealed container. .
  • the body portion 52 of the annular member 50 suppresses the collision of the swirling flow with the oil in the oil reservoir space 5, thereby suppressing the scattering of the oil. can. Since the body portion 52 of the annular member 50 is formed with the air guide wall 54, the oil existing in the annular member upper space 60 is rectified by the air guide wall 54 while being contained in the refrigerant. The oil is positively led to the oil reservoir space 5 via the passage hole 53. The refrigerant containing oil that has flowed into the oil sump space 5 separates the oil while swirling in the oil sump space 5 , and the separated oil is stored in the oil sump space 5 .
  • the oil existing in the annular member upper space 60 flows along with the swirling flow in the annular member upper space 60 while being contained in the refrigerant, and collides with the air guide wall 54 to hit the air guide wall 54. adhere to.
  • the oil adhering to the air guide wall 54 falls along the air guide wall 54 from the passage hole 53 into the oil reservoir space 5 by its own weight.
  • the airflow guide wall 54 is provided in contact with the rotation direction R side of the electric motor rotor 16a in the peripheral portion of the passage hole 53 . If the wind guide wall 54 were provided in contact with the side opposite to the rotation direction R, the swirl flow of the refrigerant containing the oil would be blocked by the wind guide wall 54 and the swirl flow could be guided to the passage hole 53 . Can not. On the other hand, since the wind guide wall 54 is provided in contact with the rotation direction R side, the wind guide wall 54 can guide the swirl flow to the passage hole 53 .
  • the compressor 100 suppresses oil splashing in the oil sump space 5 by the body portion 52 of the annular member 50 , while the oil existing in the annular member upper space 60 is directed to the air guide wall 54 and the passage hole. 53 can positively lead to the oil reservoir space 5. Therefore, the compressor 100 can reduce the amount of oil discharged to the outside of the sealed container.
  • the annular member 50 is formed by processing a plate-like member, and since the body portion 52 and the wind guide wall 54 are integrally formed, a plurality of baffle plates are fixed to the annular member. Compared to the conventional structure, the number of parts can be reduced. In this manner, the compressor 100 can reduce the amount of oil discharged to the outside of the sealed container while reducing the number of parts.
  • the air guide wall 54 straightens the swirling flow of the oil-containing refrigerant toward the passage hole 53 and actively guides the oil to the oil reservoir space 5. A higher effect of reducing the amount of oil discharged to the outside of the sealed container can be expected.
  • FIG. 6 is a partial schematic perspective view of the annular member of the compressor according to Embodiment 1.
  • FIG. 6 a flow path surrounded by an end AB on the side opposite to the rotation direction R of the air guide wall 54 and an end CD on the side opposite to the rotation direction R of the passage hole 53, that is, ABCD
  • the channel surrounded by is defined as a capture channel 55, and its area is defined as S1.
  • S2 be the area of the flow path formed by the passage hole 53, that is, the area of the flow path surrounded by the EFCD.
  • the refrigerant swirling in the annular member upper space 60 is guided from the capture channel 55 to the passage hole 53 as indicated by arrows w1 and w2.
  • the compressor 100 preferably satisfies S1>S2 in order to "capture the swirling refrigerant” and “actively return the oil to the oil reservoir space 5 by contraction".
  • S1 ⁇ S2 the structure of S1 ⁇ S2 is illustrated for convenience of illustration.
  • the compressor 100 can efficiently capture the swirling refrigerant in the capture channel 55 , and the refrigerant is contracted from the capture channel 55 toward the passage hole 53 to flow into the oil sump space 5 . Active return of oil can be achieved.
  • the angle formed by the annular member 50 and the baffle wall 54 is ⁇
  • the length of the lower side of the baffle wall 54 that is, the length between EF
  • the distance between the lower side and the upper side of the baffle wall 54 is
  • L be the length of , that is, the length between AE
  • S1 T ⁇ L ⁇ 2 sin( ⁇ /2) (Formula 1)
  • S2 T ⁇ L (Formula 2) It can be expressed as.
  • ⁇ can be derived as ⁇ >60° by substituting Equations 1 and 2 into this inequality. However, if .theta. is 90.degree. If ⁇ is 90°, the wind guide wall 54 will block the swirling flow. If ⁇ exceeds 90°, the swirling flow will flow along the upper surface of the baffle wall 54 and the flow in the annular member upper space 60 will become aggressive. Therefore, the range of ⁇ can be defined as 60° ⁇ 90°.
  • the compressor 100 includes the sealed container 1 having the oil reservoir space 5 at the bottom, the compression mechanism 2, the electric motor 16, and the drive shaft 19.
  • the compressor 100 has a plate-like body portion 52 formed with a through hole 51 through which the drive shaft 19 passes. and a plate-shaped annular member 50 arranged between.
  • the body portion 52 of the annular member 50 has a passage hole 53 through which the refrigerant above the annular member 50 passes through the lower portion of the annular member 50, and a plate-like member through which the refrigerant above the annular member 50 is guided to the passage hole 53.
  • the main body portion 52 and the wind guide wall 54 are integrally formed.
  • the compressor 100 suppresses oil splashing in the oil sump space 5 by the main body portion 52 of the annular member 50 , while the oil existing above the annular member 50 is directed to the air guide wall 54 and the passage hole. 53 can positively lead to the oil reservoir space 5. Therefore, the compressor 100 can reduce the amount of oil discharged to the outside of the sealed container. Moreover, since the body portion 52 and the air guide wall 54 are integrally formed in the annular member 50, the number of parts can be reduced compared to the conventional structure in which a plurality of baffle plates are fixed to the annular member 50. In this manner, the compressor 100 can reduce the amount of oil discharged to the outside of the sealed container while reducing the number of parts.
  • the wind guide wall 54 is formed so as to protrude from the body portion 52 toward the electric motor 16 side.
  • the air guide wall 54 can guide the coolant above the annular member 50 to the passage hole 53 .
  • the wind guide wall 54 is provided in contact with the peripheral edge portion of the passage hole 53 on the rotational direction side of the electric motor 16 .
  • the wind guide wall 54 can guide the swirling flow generated above the annular member 50 to the passage hole 53 without blocking it.
  • the air guide wall 54 is a plate-like wall formed by cutting and raising a part of the main body 52 , and the passage hole 53 is formed by a hole formed in the main body 52 by cutting and raising the air guide wall 54 .
  • the wind guide wall 54 and the passage hole 53 are formed by the above configuration.
  • the angle ⁇ of the baffle wall 54 with respect to the main body 52 satisfies 60° ⁇ 90°.
  • the air guide wall 54 can obtain the straightening property of the refrigerant to the oil reservoir space 5 .
  • the area of the flow path surrounded by the end of the air guide wall 54 opposite to the rotational direction R and the end of the passage hole 53 opposite to the rotational direction R is defined as S1, When the area of the passage hole 53 is S2, S1>S2 is satisfied.
  • the compressor 100 can capture the whirling refrigerant and positively return the oil to the oil reservoir space 5 by contraction.
  • Embodiment 2 differs from the first embodiment in the shapes of the air guide wall 54 of the annular member 50 and the through holes 53 .
  • the following description will focus on the differences of the second embodiment from the first embodiment, and the configurations not described in the second embodiment are the same as those in the first embodiment.
  • FIG. 7 is a partial schematic perspective view of the annular member of the compressor according to Embodiment 2.
  • FIG. The through hole 153 of the annular member 150 of the second embodiment has a shape in which both ends of an arc shape are connected by straight lines when viewed in the axial direction, and is in contact with the arc portion of the through hole 153, and is in contact with the through hole 153 when viewed in the axial direction.
  • a wind guide wall 154 is formed to cover 153 .
  • the wind guide wall 154 is formed by a semi-dome-shaped projecting wall formed by press working or the like.
  • the baffle wall 154 has an arcuate fixed edge 154a connected to and fixed to the main body 152 and a non-fixed edge 154b separated from the main body 152 .
  • the baffle wall 154 is surrounded by a non-fixed edge 154b, which is the end opposite to the rotational direction R of the baffle wall 154, and an edge 153a of the passage hole 153, which is opposite to the rotational direction R.
  • a capture channel 155 is formed by a region, here, a region in which both ends of an arc are connected by straight lines.
  • the air guide wall 154 guides the coolant that has flowed into the capture channel 155 to the passage hole 153 .
  • the wind guide wall 154 has a portion of the periphery of the passage hole 153 other than the edge 153a on the side opposite to the rotation direction R side, i.e., an arcuate shape in this example. located adjacent to the part.
  • the baffle wall 154 has a shape in which the length of an arc in an arc cross section obtained by cutting the baffle wall 154 along a plane extending in the radial direction becomes shorter toward the rotation direction R side and becomes 0 at the end on the rotation direction R side. have As a result, the air guide wall 154 forms a flow path between the passage hole 153 and the cross-sectional area of the flow path cut in the axial direction decreases toward the rotation direction R side.
  • the air guide wall 54 is formed by cutting and raising, so that a gap is formed between the air guide wall 54 and the passage hole 53 to allow the coolant to flow in the radial direction.
  • the air guide wall 154 is formed by press working or the like, and is in contact with a portion of the peripheral edge of the passage hole 153 other than the edge 153a on the side opposite to the rotation direction R side. Since it is provided in such a manner that it does not allow the coolant to flow in the radial direction.
  • the second embodiment can guide the coolant that has flowed into the capture channel 155 to the passage hole 153 without escaping in the radial direction after colliding with the air guide wall 154 . Therefore, in the second embodiment, the flow of the refrigerant in the radial direction is dammed by the air guide wall 154 to improve the rectification of the refrigerant, and the refrigerant containing oil can be more positively guided to the passage holes 153. As a result, It is possible to reduce the amount of oil discharged out of the sealed container.
  • FIG. 6 shows the half-dome-shaped baffle wall 154
  • the shape of the baffle wall 154 is not limited to the half-dome shape as long as the same function can be obtained.
  • the air guide wall 154 covers the passage hole 153 when viewed in the axial direction, and is in contact with the peripheral edge portion of the passage hole 153 other than the edge portion 153a on the side opposite to the rotation direction R side. It is sufficient if it has a configuration provided for
  • the rectification of the refrigerant can be further improved, and the amount of oil discharged to the outside of the sealed container can be further reduced.
  • the flow in the annular member upper space 60 is a swirling flow, and if the intention is to return the oil to the oil reservoir space 5, such as shown in FIG. It is not limited to a vertical scroll compressor having a compliant frame.
  • the compressor 100 to which the above technology is applied may be a vertical scroll compressor that does not have a compliant frame.
  • Embodiment 3 relates to a refrigeration cycle apparatus such as an air conditioner in which compressor 100 of Embodiment 1 or Embodiment 2 is mounted.
  • FIG. 8 is a schematic configuration diagram of a refrigeration cycle apparatus according to Embodiment 3.
  • the refrigeration cycle device 200 includes a compressor 100 , a four-way switching valve 103 connected to the discharge side of the compressor 100 , and an outdoor heat exchanger 104 .
  • the refrigeration cycle device 200 further includes a decompressor 105 a and a decompressor 105 b such as electric expansion, an indoor heat exchanger 106 , and a gas-liquid separator 107 .
  • the refrigerating cycle device 200 forms a refrigerating circuit in which these devices are sequentially connected via pipes. Outdoor heat exchanger 104 and indoor heat exchanger 106 function as condensers or evaporators by switching four-way switching valve 103 .
  • the four-way switching valve 103 can be omitted in the refrigeration cycle device 200 . Therefore, the refrigeration cycle device 200 may be configured to include the compressor 100 , the condenser, the pressure reducer, the evaporator, and the gas-liquid separator 107 .
  • the gas-liquid separator 107 separates the inflowing two-phase refrigerant into saturated gas refrigerant and saturated liquid refrigerant.
  • the gas-liquid separator 107 has an injection pipe 110, which is a gas outflow pipe for discharging the separated saturated gas refrigerant to the outside.
  • a downstream end of the injection pipe 110 is connected to the compressor 100 .
  • An on-off valve 111 for opening and closing the injection pipe 110 is connected to the injection pipe 110 .
  • the four-way switching valve 103 In heating operation when the refrigeration cycle device 200 is applied to, for example, an air conditioner, the four-way switching valve 103 is connected to the solid line side in FIG.
  • the high-temperature, high-pressure refrigerant compressed by the compressor 100 flows into the indoor heat exchanger 106, where it is condensed and liquefied. After that, the two-phase refrigerant flows into the gas-liquid separator 107 .
  • the saturated liquid refrigerant separated by the gas-liquid separator 107 passes through the pressure reducer 105a, flows to the outdoor heat exchanger 104, evaporates, and is gasified.
  • the gasified refrigerant passes through the four-way switching valve 103 and returns to the compressor 100 again.
  • the refrigerant in heating operation, the refrigerant circulates as indicated by the solid line arrows in FIG. Due to this circulation, the refrigerant exchanges heat with the outside air in the outdoor heat exchanger 104, which is an evaporator, and absorbs heat. The refrigerant that has absorbed heat is sent to the indoor heat exchanger 106, which is a condenser, and exchanges heat with the indoor air to warm the indoor air.
  • the four-way switching valve 103 In cooling operation when the refrigeration cycle device 200 is applied to, for example, an air conditioner, the four-way switching valve 103 is connected to the dashed line side in FIG.
  • the high-temperature and high-pressure refrigerant compressed by the compressor 100 flows to the outdoor heat exchanger 104, is condensed and liquefied, and is then decompressed by the pressure reducer 105a into a low-temperature and low-pressure two-phase state. influx.
  • the saturated liquid refrigerant separated by the gas-liquid separator 107 flows through the pressure reducer 105b to the indoor heat exchanger 106, where it evaporates and gasifies.
  • the gasified refrigerant passes through the four-way switching valve 103 and returns to the compressor 100 again.
  • the refrigerant circulates as indicated by the dashed arrows in FIG. Due to this circulation, the refrigerant exchanges heat with indoor air in the indoor heat exchanger 106, which is an evaporator, and absorbs heat from the indoor air. This cools the indoor air.
  • the refrigerant that has absorbed heat is sent to the outdoor heat exchanger 104, which is a condenser, exchanges heat with the outside air, and radiates heat to the outside air.
  • the refrigeration cycle apparatus 200 configured in this manner can reduce the amount of oil rising from the compressor 100 and improve reliability by including the compressor 100 of the first embodiment or the second embodiment.
  • the refrigerant circuit of FIG. 8 has pressure reducers on both upstream and downstream sides of the gas-liquid separator 107, and is a refrigerant circuit in which the gas-liquid separator 107 is used at an intermediate pressure. In such a refrigerant circuit, an excessive amount of oil exists in the gas-liquid separator 107, and it is considered that an oil return device is required to prevent the excessive oil from being returned to the sealed container 1. Since the refrigerating cycle device 200 includes the compressor 100 described above, the oil can be positively returned to the oil reservoir space 5 inside the compressor, so an oil return device is unnecessary.
  • the refrigeration cycle device 200 can be applied to a refrigerator, a freezer, a refrigerating device, a water heater, etc., in addition to the air conditioner.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)

Abstract

Un compresseur (100) comprend : un récipient étanche (1) possédant un espace de réservoir d'huile dans une section inférieure de celui-ci ; une unité de mécanisme de compression (2) qui est disposée à l'intérieur du récipient étanche et qui comprime un fluide frigorigène ; un moteur électrique (16) qui est disposé dans la partie inférieure de l'unité de mécanisme de compression ; et un arbre d'entraînement (19) qui transmet une force de rotation du moteur électrique à l'unité de mécanisme de compression. Le compresseur comprend en outre : un élément annulaire en forme de plaque (50) qui possède une section de corps en forme de plaque (52) dans laquelle un trou débouchant, à travers lequel passe l'arbre d'entraînement, est formé, l'élément annulaire en forme de plaque étant disposé, l'arbre d'entraînement passant à travers le trou débouchant, entre le moteur électrique et une huile qui a été collectée dans l'espace de réservoir d'huile. Formés dans la section de corps de l'élément annulaire se trouvent : un trou débouchant (53) à travers lequel le fluide frigorigène au niveau de la partie supérieure de l'élément annulaire passe vers la partie inférieure de l'élément annulaire, et une paroi de vent avant en forme de plaque (54) qui guide le fluide frigorigène au niveau de la partie supérieure de l'élément annulaire dans le trou débouchant. La section de corps et la paroi de vent avant sont formées d'un seul tenant l'une avec l'autre.
PCT/JP2022/005282 2022-02-10 2022-02-10 Compresseur et dispositif de cycle de réfrigération WO2023152854A1 (fr)

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001050162A (ja) * 1999-08-10 2001-02-23 Mitsubishi Heavy Ind Ltd 密閉型圧縮機
KR20060120386A (ko) * 2005-05-19 2006-11-27 엘지전자 주식회사 스크롤 압축기의 유분리 장치
JP2013217281A (ja) * 2012-04-09 2013-10-24 Mitsubishi Electric Corp ロータリー式圧縮機

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001050162A (ja) * 1999-08-10 2001-02-23 Mitsubishi Heavy Ind Ltd 密閉型圧縮機
KR20060120386A (ko) * 2005-05-19 2006-11-27 엘지전자 주식회사 스크롤 압축기의 유분리 장치
JP2013217281A (ja) * 2012-04-09 2013-10-24 Mitsubishi Electric Corp ロータリー式圧縮機

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